Thompson
indexing device



June 6, 1967 E. A. THOMPSON Re. 26,218

INDEXING DEVICE Original Filed March 14, lQGO 4 Sheets-Sheet 1 INVENTOR.

EArgATHoMPsoN ATTO/WE) June 6, 1967 E. A. THQMPSON Re. 26,218

INDEXlNG DEVI CE Original Filed March 14, 1960 4 Sheets-Sheet 2 IN VENTOR.

EA I' Q L A. THOMPSON Mf /1 a ATTORNEY June 6, 1967 THOMPSON Re. 26,218

INDBXING DEVICE Original Filed March 14, 1960 4 Sheets-Sheet 5 EAgLATHOMPS ON WKTMM ATTORNEY June 6, 1967 A. THOMPSON INDEXING DEVICE 4Sheets-Sheet 4 Original Filed March 14, 1960 INVENTOR. EAE L ATHOMPSON wA A? /M.A

ATTORNEY United States Patent Original No. 3,118,347, dated Jan.

14,630, Mar. 14, 1960. Application 1966, Ser. No. 527,641

12 Claims. (CI. 90-56) lvlatter enclosed in heavy brackets II] appearsin the original patent but forms no part of this reissue specification;matter printed in italics indicates the additions made by reissue.

This is a continuation-in-part of this inventors copending and nowabandoned application Serial Number 706,181 filed December 30, 1957.

The invention relates to 21, 1964, Ser. No. for reissue Jan. 18,

work performing station to or that of an endless chain a sprocket.

another around its periphery, for which the member acts as accuracy andrigidity not only with respect to angular position but also as toconcentricity with its rotating axis. his problem is particularlytroublesome maintained with reasonable accuracy.

Accordingly, it is an object of the present invention to expensiveapparatus.

A further object is to provide an improved rotary table indexing machinein which a high degree of positioning ting cam motions to the drivenparts.

A further object is to provide an improved rotary table indexing machineon which a sequence of movements conditioning the table for an indexingmovement may be made sequentially in a minimum amount of time, and byRe. 26,218 Reissued June 6, 1967 a single actuating mechanism which willrepeat the sequential movements accurately every time.

object is to provide an improved rotary forming tools placed around theperiphery of the table with extreme accuracy and with mechanism thatwill not lose its effectiveness over a long, useful life.

Further objects and advantages of the present invention will be apparentfrom the following detailed description with reference to theaccompanying drawings, in

FIGURE 1 is a top view with parts broken away of a rotary table indexingmachine embodying a preferred form of the present invention;

FIGURE 2 is a vertical cross section taken along the line 22 of FIGURE1;

FIGURE 3 is an enlarged view of the table raising mechanism shown at thebottom of FIGURE 2;

FIGURE 4 is an enlarged vertical sectional view of the locatingmechanism shown at the right hand portion of FIGURE 2; and

FIGURE 5 is a diagrammatic view of a mechanicohydraulic programming anddrive system for operating the machine shown in FIGURES l and 2.

Referring now to FIGURES l and 2, there is shown a rotary table 10 whichnormally rests on a frame or base of the machine 18 slight outwardflexing of wall and 22 assures, with any 16 as surface 22 descends andsupporting surfaces, :1 table outside cise fitting of the centering lip25 is provided on the underside of the the wall 16.

The rim of the table 10 containing surfaces 22 is supported by means ofa central web portion 26 fixed set of bearings 34 at its lower end.Bearings 34 are fitted on a reduced diameter portion 36 of the shaft 28and secured thereon by locking nut 38, see FIGURE 3.

The outer race of the lower bearings 34 is contained in an annularsliding sleeve member 40 fitted within a smooth bore 42 in a housing 44depending from the base 12. Bore 42 is closed at its upper end by anapertured member 46 through which the shaft 28 extends and which alsoserves to govern the amount of upward sliding of which the sleeve member40 is capable. Secured to the lower end of the sleeve member 40 bysuitable bolts 46 is a piston face or head unit 48 adapted to receivethe inner diameter of a Belleville spring in a suitable annular groove52. Belleville spring 50 is secured at its outer diameter to thedepending housing 44 by means of a lower closure member 54 securedthereto by bolts or other suitable securing means 56. Lower closuremember 54 is cored out to form a cavity 58 of a size large enough toinclude both the head unit 48 and a suitable fluid cavity around it. Oilor other fluid is admitted to this cavity through a connection 60.

Belleville spring 50 is loaded to continually urge shaft 28 downwardly,and this downward urging is limited only by the contact of surfaces 18,22 and 20, 24, respectively, at the periphery of the table. When oilunder pressure is admitted through the connection 60 and into the cavity58 between the member 54 and the unit 48, the upward pressure on member48 and on the spring 50 causes the shaft 28 to move upwardly against thedownward urging of the spring and raise the surfaces 22, 24 away fromthe surfaces 18, 20, respectively, and thus position the table for freerotation on its shaft 28 within the bearings 30, 34.

The rotating means comprises an arm '70 mounted for rotation at 72 aboutthe shaft 28 which is also the tables axis of rotation. Gear segments 74concentric with the shaft 28 at the inner end of the arm engage theteeth 76 of two opposed racks 78 formed as part of two pistons 80 whichare alternately reciprocable in cylinder sections 82. The two pistons 80in their cylinder sections 82 comprise a double acting hydraulic motorwhich acts, as oil under pressure is admitted through connection 84, toswing arm 70 clockwise (FIGURE 1) and return it counter clockwise as oilis admitted through connection 86. The length of oscillation of arm 70is governed by two adjustable limit stops 88 positionable anywherearound a track 90 which is formed as part of the base 12.

Within a bore in the arm 70 is a plunger 92 having a tooth or finger 94at its outer end which is urged by a spring 96 inwardly toward the armsaxis of oscillation.

The inner end of the plunger 92 fits within a cylinder 98 and is formedas a piston 100. Oil under pressure is admitted to cylinder 98 by meansof a bore 102 in the arm which communicates with suitable bores 104 inthe shaft 28 to which oil is in turn introduced by other passages 106 inthe housing 44 (see FIGURE 2) from the connection 60 which also admitsoil to the cavity 58 for raising the table.

Around the periphery of table 10 is mounted a ring gear having veryaccurately cut teeth 108. The gear is secured to the table by means ofbolts 110 extending through holes in the gear. By utilizing a pluralityof holes, the gear can be rebolted to the table in different positionsto expose new and unworn teeth to the finger 94 of the rotating means inorder that precision indexing be maintained through a long and usefullife of the machine. Admission of oil under pressure to the cylinder 98in the arm 70 will extend the plunger 92 until the finger 94 on the endof the plunger is snugly engaged with the teeth 108 of the ring gear. Assoon as this engagement is established, admission of oil to one of thecylinders 82 through connection 84 will oscillate the arm 70 in onedirection between the limit stops 88, and the table 10 will rotatetherewith as a result of the connection established between the finger92 on the arm and the teeth 108 on the tables ring gear.

r through the This can take place quite rapidly, say in less than 2% ofa second, for instance, for sixty degrees of angular movement.

After the table has been indexed by oscillation of the arm 70 until itcontacts its limit stop 88, the table must be accurately locatedangularly so that the workpieces will be precisely positioned inrelation to the tools around the edge of the table before the table islowered to center and support itself on the surfaces 18 and 20 on thebase. The workpieces are positioned in sockets 112 which have anenlarged portion at their top to receive the workpiece and a taperedportion at the bottom. These sockets 112 are formed in brackets 114adiustably secured to the table by means of bolts 116 at equi-angularlyspaced locations in a circle concentric with the tables rotating axis.Directly below the sockets 112 in brackets 114 there are holes 118 inthe table of a diameter somewhat larger than the outer diameter of thetapered portion of the socket (see FIG- URE 4).

Positioned directly below one of the work stations 14, probably the onewhich would require the most accurate locating of the workpiece, is thelocating mechanism 120 which consists of a piston 122 reciprocable incylinder sections 124, 126 and having extending upwardly therefrom apiston rod 128 with a tapered end 130. The tapered end is accuratelyguided for reciprocation in a replaceable sleeve 132. Oil under pressureadmitted through connection 134 to the lower face of piston 122continually urges the piston upwardly and the tapered locating endportion 130 through the hole 118 in the table and into the taperedportion of the workpiece socket 112. Thus the workpiece socket .112 inthe bracket 114 is the member that is actually positioned by thelocating device 120, and not the table itself which is subject todimensional variations as a result of temperature changes, forcesoccasioned by the thrust of various tools 14, and other influences.

When the table is to be rotated, oil is admitted through connection 136to the upper face of the piston 122 at a pressure higher than thatadmitted through connection 134. The pressure on the upper face of thepiston 122 overcomes that against the lower face; the tapered portion130 of the locating mechanism is retracted from the tapered portion ofthe workpiece socket 112 and down hole 118 in the table, thus allowingthe table to be rotated. After the table has been raised from thesupporting surface 20 and the centering surface 18 and rotated by thearm 70, oil is allowed to drain away from the upper face of the piston122 of the locating mechanism back through connection 136, and thepiston is again raised by the pressure of the oil being admitted throughconnection 134 until the tapered portion 130 has accurately located theworkpieces. Then, as the table is lowered onto its centering andsupporting surfaces 18 and 20, respectively, the piston 122 is alsoforced downwardly a small amount therewith, insuring an even morepositive locating association of the tapered portion 130 in the taperedportion of the workpiece socket 112.

Since, prior to angular indexing of the table 10, it is desirable tohave the table raised from its centering and supporting surfaces 18, 20before the finger 94 engages the tables ring gear, and it is desirableto have the ring gear engaged by the finger before the locatingmechanism 130 is released from the socket; and since, after the tablehas been indexed, it is desirable to have the locating mechanism 130engage the workpiece socket before the finger 94 on the arm 70 isretracted, and it is desirable to have the finger retracted before thetable is lowered by the action of the Belleville spring 50 intoengagement with the supporting and centering surfaces, a uniquearrangement is provided to insure that this desired sequence takes placein a minimum amount of time bcfore and after each indexing of the table.This is best described by ref erence to the lower right hand corner ofHG. 5, where the three actuating mechanisms for these three sequentialmovements are shown schematically.

Belleville spring 50 is designed to urge the table toward the base witha predetermined amount of force. The spring 96 in the oscillating arm isdesigned to require more fluid pressure to overcome its power than doesthe Belleville spring 50, and to urge the finger 94 out of engagementwith the table with a force exceeding that of the spring 50. Biasingmeans 134 (which in this case is hydraulic pressure and not a spring)urges the locating mechanism 130 into engagement with the table with aforce greater than that by which the finger 94 is urged out ofengagement with the table. It will be understood that the actual springmeans, whether mechanical or hydraulic, need not themselves be of moreor less force than the other springs, but the face area of the pistons48, 100 and 122 are, in practice, of varying areas so that the effectiveforces required to overcome the springs will vary by a predeterminedamount to obtain the desired priority of movement. It will be noted fromthe diagram that the fluid admitted to the faces of these three pistonsfor overcoming the three springs or urging means is connected from eachcylinder to a single hydraulic supply line 314f.

Thus, as oil pressure in line 314f increases, Belleville spring 50 willfirst be overcome by pressure on the face of piston 48 and the tablewill be raised off of its centering and supporting surfaces. Secondly,the spring 96 will be overcome by the now high pressure of the fluid onthe face of piston and the finger 94 will engage with the ring gear onthe table. Finally, hydraulic pressure at 134 will be overcome by theaction of the still higher oil pressure on the upper face of piston 122and the locating mechanism 130 will be retracted from the workpiecesocket. This predetermined sequence will occur without fail and can,depending on how quickly oil pressure is increased in line 114,accomplish all three movements in their timed sequence in a very shortinterval.

After the table has been indexed, the required amount of oil is rapidlydrained from line 314f and, in a very short time (measured again in afraction of a second) the locating mechanism engages with the table, thearms finger is retracted from the ring gear of the table, and the tableis lowered to the centering and supporting surfaces on the base. Thenthe tools around the periphery of the table immediately commence theiroperation. It will be understood that several spring loaded fluid motorsin tandem with a single fluid pulsator unit could be used for any typeof operation where a particular priority of motion is desired.

For the purpose of giving coordinated motivation to the variousoperating means for the table and for the Work stations 14 there isprovided a mechanico-hydraulic programming system for producing a cycleof coordinated movement, illustrated diagrammatically in FIG. 5. Thissystem may be constructed as a self-contained unit having its ownhousing, not illustrated, which may be positioned at any convenientlocation on or adjacent the machine and connected to the varioushydraulic cylinders by suitable flexible piping. The mechanico-hydraulicdrive unit comprises a master camshaft 236 carrying a plurality of cams238, the followers of which operate the transmitter pistons 240, each ofwhich forms part of a liquid column type motion transfer device of whichthere are eight units shown in the diagram of FIG. 5. Each pistonreciprocates in a cylinder 242 having a head 244 which contains asuitable inlet replenishing check valve 308 and a high pressure reliefvalve 310 both of which communicate with a low pressure oil reservoir312 preferably formed in a housing enclosing the drive unit.

For turning the camshaft 236, a motor 246 drives an input shaft 248 of atwo-speed transmission through a belt drive 250. The input shaft 248drives a pinion 252 and also the input member of ahydraulically-engaged, springreleased clutch 254. Pinion 252 drives agear 256 secured to a countershaft 258 which carries a pinion 260 at itsopposite end. Pinion 260 drives a gear 262 and therewith constitutes aset of change speed gears. Gear 262 drives the input member of a secondhydraulically-engaged, spring-released clutch 264. The driven members ofclutches 254 and 264 are secured to the opposite ends of a shaft 266,having a worm 268 thereon and a brake drum 270. The latter has aspring-biased hydraulic motor 272 for engaging the brake. Worm 268drives a worm wheel 274 secured to the master camshaft 236.

For the purpose of automatically controlling the starting, stopping, andspeed of the transmission, there is provided a hydraulic control pump276 driven from gear 262, which may circulate a body of oil contained inthe housing surrounding the transmission. The pump 276 may deliver to acombined accumulator and relief valve comprising a spring loaded piston278 and also supplies oil to a bank of control valves 280, 282 and 284.In the diagrams each valve is shown as a two-position valve,springbiased to the position illustrated in which the connections shownin the crosshatched rectangles are established. Singleheaded arrows areused to indicate flow at reservoir pressure and double-headed arrows toindicate flow at pump delivery pressure. Each of the valves, whenshifted, establishes the connections shown in the unhatcbed rectanglesimmediately below the hatched rectangles.

Valve 280 is arranged to be shifted by a solenoid 286. Valves 282 and284 are arranged to be shifted by the adjustable cams 288 and 290,respectively, which are positioned on camshaft 236. In addition, thevalve 282 has a hydraulic holding cylinder 292 which holds the valve 282in its shifted position until it is released by the shifting of valve284. Valve 280 in the position shown delivers pressure fluid to engagethe brake 272 and also exhausts fluid to release the low speed clutch264. When shifted, valve 280 exhausts fluid to release brake 272 andsupplies pressure fluid to engage the low speed clutch 264, subject,however, to a conjoint control by the valve 282.

The latter valve, in the position illustrated, exhausts fluid to releasethe high speed clutch 254 and places the low speed clutch 264 under thecontrol of valve 280. In its shifted position, valve 282, provided valve280 has been shifted, delivers pressure fluid to engage high sueedclutch 254 and exhausts fluid to release low speed clutch 264. Aspreviously explained, the valve 284 is merely a reset valve forbypassing the holding cylinder 292 to permit valve 282 to return to itsspring biased position shown in the drawings.

Thus, energization of solenoid 286 will start the camshaft rotating atslow speed. Thereafter, the cam 288 will shift the transmission to drivethe camshaft at high speed, and still later the cam 290 will again shiftthe transmission to slow speed. So long as the solenoid 286 remainsenergized, the camshaft 236 will continue to rotate, first at a slowspeed and then at a high speed during each revolution, controlling itsown speed changes by operations of the cams 288 and 290.

For the purpose of controlling the drive motor 246 and solenoid 286.there is provided an electric control circuit connected between a pairof electric supply lines, designated L1 and L2. The circuit may includea master relay 294 of the holding type having a manual master startswitch 296 and a manual master stop switch 298. Relay 294 controls themotor 246 and also a cycle control relay 300 of the holding type havinga manual cycle stop switch 304. The normally open contacts of relay 300,which are of the make-beforebreak type, control energization of cyclesolenoid 286 directly. The normally closed contacts of relay 300 alsocontrol solenoid 286, but are in series with a cam switch 306 on the endof the camshaft 236 and arranged to be opened once during eachrevolution thereof. The arrangement is such that when the cycle stopswitch 304 is operated at any point in the rotation of camshaft 236,relay 300 will be de-energized, but solenoid 286 will remain energizeduntil cam switch 306 opens at the predetermined stopping point.Operation of the master stop switch 298, however, will de-energizesolenoid 286 immediately, regardless of the point in the cycle and willalso de-energize motor 246.

The camshaft 236 as previously mentioned drives a number of cam operatedhydraulic pulsator sections designated a through h, inclusive. Eachsection may com prise units duplicating the single acting pulsatingcylinder 242, the head 244 of which contains the replenishing checkvalve 308 and the spring closed release valve 310. All the replenishingand relief valves are connected to a common oil resorvoir 312 formed inthe housing of the unit. The reservoir 312 is preferably subjected to alow, super-atmospheric pressure by a body of compressed air or otherpressure maintaining arrangements. Check valves 308 allow fiow from thereservoir 312 to the cylinder 242, while relief valves 310 allow flowoppositely when the cylinder pressure exceeds a certain value. Thus eachof the pairs of valves 308 and 310 may be referred to as a balancingvalve and serve to balance the volume of fluid in each of the liquidcolumn sections, as will be later described.

The pulsator sections a and h are connected by closed liquid columnlines 314a and 314h with two of the work performing stations 14, asshown in FIGURE 5. Similarly, the closed liquid column lines for thesections c, d, e and g may be connected to others of the work performing stations. The pulsator section b is connected by a closed liquidcolumn line 314b with the connection 84 of the cylinder 82 foroscillating the arm 70 between its limit stops 88. The pulsator sectionf is connected by closed liquid column line 314f with the threesequentially operable fluid means for raising the table, engaging thearms finger, and disengaging the locating mechanism.

In order to insure proper synchronization of the driving and drivenelements of each pulsator section, it is desiraable to provide slightlymore fluid displacement in the driving or transmitting elements 240-242than is present in their respective fluid motors at the opposite end ofthe liquid column line. Thus at the end of each advancing stroke of thetransmitter piston 240, a small amount of fluid will be discharged toreservoir 312 through its relief valve 310. This amount plus any amountlost by leakage will be returned to the liquid column at the end of thereturn stroke by the operation of the replenishing valve 308.

In FIGURE 5 there are shown several circles marked R connected to theend of some of the motive cylinders opposite the liquid columnconnections. These symbols designate the return oil connections by meansof which a pulsator system may be hydraulically biased so as to maintainthe follower in close contact with the cam as the falling portion of thecam contour recedes from the follower. Consequently, the strongesturging means of the three sequential operations in the lower right-handcorner of FIGURE must be of the hydraulic type. This bias is maintainedby a high pressure accumulator or oil reservoir, not shown, which may beprovided with a manifold whereby all of the R0 connections are joinedtogether and to the high pressure reservoir. The showing of separatereturn oil connections in FIGURE 5 is indicative of any suitable type ofbiasing pressure source, whether it be a single accumulator ormultiplicity thereof. The contours of the individual cams 238 arelikewise not illustrated in specific detail since they may be formed inaccordance with the usual practice to cause motivation of each of therespective hydraulic motors in accordance with the particular operatingcycle desired for the machine. Likewise the speed ratio between the highand low speeds of the cam shaft 236, and the duration of the high speedportion of the cycle, may he selected as desired through use of theappropriate change gears 260-262 and through the adjustment of the cams288 and 290, if desired. Of course, the two speed feature of thetransmission may be omitted and the high speed clutch 254, the cams 288and 290 and the valves 282 and 284 eliminated.

In operation, with the reservoirs R0 and 312 filled with oil and with abody of compressed air at relatively respectively high and lowpressures, the master start switch 296 is closed to start the motor 246of the mechanico-hydraulic drive and control unit. A series of cyclesmay then be initiated by operation of the cycle start switch 302. Thisenergizes relay 300 which in turn energizes solenoid 286 to shift thestarting valve 280 and cause operation of the cam shaft 236 at its slowspeed as previously explained; during the slow speed portion of thecycle the various work performing stations 14 may be operated from thepulsator units.

When these operations have been completed, the rapid speed cam 288 willshift the valve 282 which will be held in a shifted position by cylinder292, thus causing the master cam shaft 236 to rotate at rapid speeds,being driven through clutch 254 instead of clutch 264. Thereafter thefirst event will be the lifting of the work table from its conicalcentering surface and at supporting surface by the initial action of thepulsator section f; as the pulsator section f continues its action, thefinger 94 will then engage the teeth on the gear 108 of the table; and,finally, the locating mechanism .130 will be retracted from the workpiece socket on the table. The table 10 is then supported upon spindleshaft 28 for rotation in the bearings 30, 34 and on the oil in cavity58. As the action of pulsator section f is being completed, pulsatorsection b will come into action to cause reciprocation of the pistons intheir cylinders 82, and the racks 78 will oscillate the arm 70 betweenits limit stops 88, thus rotating the table 10 to a position in whichthe next socket 112 is over the locating mechanism The acceleration anddeceleration involved in table rotating movement may be of anycharacteristic desired, as determined by the contour of the cam 238 forthe pulsator section b. When this movement has been completed, thepulsator section f presents a receding cam face to the follower andpressure is relieved in line 314i, causing the locating mechanism to beengaged with the table, the finger 94 to be retracted from engagementwith the table, and the table to lower on the centering and supportingsurfaces 18, 20, respectively, on the base, thus positioning the tablefor the commencement of the work operations which are powered andcontrolled by the other cams in the powering and controlling unit. Thereturn of racks 78 to their starting positions may be accomplishedduring the slow speed portion of the cycle while the work stations 14are performing their work and while the finger 94 is retracted fromengagement with the table.

The operation above described will be repeated for each successiverevolution of the master cam shaft 236, which continues in operationuntil the stop switch 304 is operated. As previously explained, thiswill bring the cam shaft to rest in its normal stopping positiondetermined by the cam switch 306.

It will thus be seen that the present invention provides an improvedrotary indexing table machine in which the timing of the index and dwellportions of the machine cycle is free of the severe design limitationsinherent in Geneva gearing, and in which the mechanism is simple,reliable and exible. Furthermore, the device provides a rotary tablewhich is rigidly mounted when in the dwell phase of its cycle and may beutilized to accurately position parts while subjected to substantialthrust against the table and in which the various motions involved inindexing the table between work performing operations is accomplished ina minimum amount of time.

While the above described embodiment constitutes a preferred mode ofcarrying out this invention, many other forms might be adopted withinthe scope of the actual invention, which is variously claimed as:

1. A rotary indexing machine comprising a base, a table mounted forintermittent rotary motion relative to the base, an upstanding wall onsaid base, a centering surface bevelled on said wall, a supportingsurface formed in a fiat plane on said [wall] bdse, two surfaces on thetable and near the periphery thereof compatible with said centeringsurface and said supporting surface respectively, and means for axiallymoving said compatible surfaces, apart [during] before rotary motion ofthe table and bring said compatible surfaces into mating contact duringintermissions in rotary motion to center as well as support the table.

2. An indexing machine comprising a base, a plurality of work performingmechanisms mounted at spaced stations on the base, a table mounted onthe base for intermittent movement, sockets on said table for holdingworkpieces and carrying them seriatirn to the stations, a locating pinon said base designed to extend into any one of said workpiece socketsto lock the table relative to the base, and means to so extend the pinduring intermissions in table movement.

3. A rotary indexing machine comprising a frame having a main pivtoalsupport, a rotary table pivoted on said support, a suplementarysupporting means comprising mating [circular] surfaces [of] arranged inrings which are large [diameter] relative to the main support andlocated on the frame and table respectively, means for intermittentlyindexing the table through successive angular movements, means operatingin timed c-o-ordination with the indexing means for raising the tableclear of its mating [the] supplementary support surface before eachendexing movement and lowering it between successive movements, and amechanico-hydraulic motivator connected to operate each of said means,the motivator including a plurality of rotary cams driven in unison, asingle-acting expansible chamber type pulse transmitter driven by eachcam, a plurality of double-acting expansible chamber type pulsereceivers connected with the said means, a plurality of liquid columnsconnected between the transmitters and the receivers to transfer motiontherebetween, and a source of pressurized fluid and means connecting itto the receivers in opposition to the liquid column connections tocounter-bias cam actuation.

4. A rotary indexing machine comprising a frame having a main pivotalsupport, a rotary table pivoted on said support, means forintermittently indexing the table through successive angular movements,a plurality of work performing tool carriers mounted on the frame andjuxtaposed to the table at spaced work stations, and amechanico-hydraulic motivator comprising a common rotary driving device,a pjlurality of cams connected to be rotated thereby and a plurality ofliquid column type motion transfer devices each driven by a cam andconnected to drive said indexing means and each of said tool carriersthrough a coordinated program of movements each revolution of saiddriving device.

5. A rotary indexing machine comprising a frame having a main pivotalsupport, a rotary table pivoted on said support, a supplementarysupporting means comprising mating [circular] surfaces [of] arranged inrings which are large [diameter] relative to the main support andlocated on the frame and table respectively, means for intermittentlyindexing the table through successive angular movements, means operatingin timed co-ordination with the indexing means for raising the tableclear of its mating [the] supplementary support surface before each[indexing] angular movement and lowering it between successivemovements, a plurality of Work performing tool carriers mounted on theframe and juxtaposed to the table at spaced work stations, and amechanico-hydraulic motivator comprising a common rotary driving device,a plurality of cams connected to be rotated thereby and a plurality ofliquid column type motion transfer devices each driven by a cam andconnected to drive each of said means and each of said tool carriersthrough a coordinated program of movements each revolution of saiddriving device.

6. A rotary indexing machine comprising a table mounted for rotarymovement, a mechanism for indexing the table through a predeterminedangle, a plurality of work performing mechanisms mounted at spacedstations around the table and a common programming and driving systemfor the table and the mechanisms, including a camshaft, means fordriving the camshaft through one revolution for each program cycle,individual cams on the shaft for each mechanism, and individual liquidcolumn type motion transfer devices connected between each cam and itsmechanism whereby the camshaft may drive the table indexing mechanismthrough one portion of a camshaft revolution and the Work performingmechanisms through another part of a revolution.

7. A rotary indexing machine comprising a table mounted for rotarymovement, a mechanism for indexing the table through a predeterminedangle, a plurality of work performing mechanisms mounted at spacedstations around the table, a stationary rigid support for the tablehaving contact therewith near the table periphery, mechanism for raisingthe table off the support [while] before being moved, [indexed] and acommon programming and driving system for the table and the mechanisms,including a camshaft, means for driving the camshaft through onerevolution for each program cycle, individual cams on the shaft for eachmechanism, and individual liquid column type motion transfer devicesconnected between each cam and its mechanism whereby the camshaft maydrive the table indexing mechanism through one portion of a camshaftrevolution and the work performing mechanisms through another part of arevolution.

8. A rotary indexing machine comprising a table mounted for rotarymovement, a mechanism for indexing the table through a predeterminedangle, a plurality of work performing mechanisms mounted at spacedstations around the table and a common programming and driving systemfor the table and the mechanisms, including a camshaft, means fordriving the camshaft through one revolution for each program cycle,means controlled by the camshaft for changing the drive speed thereofduring each revolution, individual cams on the shaft for each mechanism,and individual liquid column type motion transfer devices connectedbetween each cam and its mechanism whereby the camshaft may drive thetable indexing mechanism through one portion of a camshaft revolutionand the work performing mechanisms through another part of a revolution.

9. A rotary indexing machine comprising a frame member having a mainpivotal support, a rotary table member pivoted on said support, means,including a hydraulically shiftable rack arrangement on one member and apinion arrangement connecting it with the other member, forintermittently indexing the table member through successive angularmovements, a hydraulic means associated with the pinion arrangement fordisconnecting the rack arrangement and the other member so that the rackarrangement may be reset, and a mechanico-hydraulic motivator comprisinga common camshaft and a plurality of liquid column type motion transferdevices connected to operate each of said means.

10. A rotary indexing machine comprising a frame member having a mainpivotal support, a rotary table member pivoted on said support, means,including a hydraulically shiftable rack arrangement on one member and apinion arrangement connecting it with the other member, forintermittently indexing the table member through successive angularmovements, a hydraulic means associated with the pinion arrangement fordisconnecting the rack arrangement and the other member so that the rackarrangement may be reset, a [table lock pin] table locking means alsooperated in conjunction with the last named hydraulic means, and amechanico-hydraulic motivator comprising a common camshaft and aplurality of liquid column type motion transfer devices connected tooperate each of said means.

II. An indexing machine comprising a base, a plurality of workperforming mechanisms mounted at spaced stations on the base, a tablemounted on the base for intermittent movement, work holders on the tablefor holding workpieces and carrying them seriatim to the stations, firstlocating means on each work holder and second locating means on the basedesigned to engage any one of the first locating means to locate thework holder with reference to the base and to lock the table to the bse, and means for engaging the second and a first locating means duringintervals between table movement.

12. A rotary indexing machine comprising a frame having a main pivotalsupport, a rotary t ble pivoted on said support, a supplementarysupporting means comprising mating surfaces arranged in rings which arelarge relative to the main support and located on the frwme and tablerespectively, means including a hydraulically shiftable rack and apinion connected with the table for intermittently indexing the tablethrough successive angular movements, and a hydraulic me ns fordisconnecting the pinion from the table so that the rack may be reset.

References Cited The following references, cited by the Examiner, are

of record in the patented file of this patent or the original patent.

UNITED STATES PATENTS 658,557 9/ 1900 Pitt.

912,124 2/1909 Hanson. 1,209,708 12/1916 Houlehan. 1,288,966 12/1918Nielsen. 1,881,185 10/1932 Hazelton. 2,051,720 8/1936 Kingsbury.2,120,877 6/ 1938 Uber. 2,135,639 11/ 1938 Gotham. 2,153,637 4/1939Niven. 2,429,938 10/1947 Mansfield. 2,560,475 7/1951 Rehnberg et 211.2,588,977 3/1952 Gartner et 211. 2,622,487 12/ 1952 Shultz. 2,715,9448/1955 Dohrer. 2,842,985 7/1958 Grover. 2,900,849 8/1959 I-Iutchens et211. 2,952,169 9/1960 Johnson. 2,975,657 3/1961 Samuel.

WILLIAM W. DYER, JR., Primary Examiner.

G. A. DOST, Assistant Examiner.

